CN111981064B

CN111981064B - Brake cylinder with locking device for mechanical brake force locking

Info

Publication number: CN111981064B
Application number: CN202010439509.1A
Authority: CN
Inventors: M·玛蒂厄; F·黑希特
Original assignee: Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Current assignee: Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Priority date: 2019-05-24
Filing date: 2020-05-22
Publication date: 2022-05-27
Anticipated expiration: 2040-05-22
Also published as: DE102019113930A1; EP3744592B1; CN111981064A; EP3744592A1; ES2925276T3

Abstract

The invention relates to a brake cylinder, in particular for a rail vehicle, comprising: a locking device for mechanical brake force locking; and a service brake piston which is axially movable in the housing and which can be moved by a pressurized medium and which engages with the piston tube, wherein the piston tube is designed with a non-self-locking thread which engages with a nut which is rotatably mounted in the housing, wherein a locking device interacts with a toothing of the nut, wherein the locking device has one or more pawls, a control piston, an emergency release mechanism and a locking element of the emergency release mechanism, and the brake cylinder is designed in such a way that the locking device (10) has an operating device (14) which comprises the control piston (16), the emergency release mechanism in the form of an emergency release wedge (15), at least one locking element (17), at least one energy storage element (18) and a connecting means (21) for manual release.

Description

Brake cylinder with locking device for mechanical brake force locking

Technical Field

The invention relates to a brake cylinder having a locking device for mechanical brake force locking.

Background

Rail vehicles are equipped with such brake cylinders. The rail vehicle in parking must be stopped to prevent rolling. For this purpose, a parking brake is provided with an auxiliary brake cylinder, which must ensure a correspondingly high braking force even without the supply of an external energy source.

Such brake cylinders of rail vehicles must meet the following specifications:

-arresting the vehicle against unintended rolling;

-continuously ensuring the necessary braking force independently of the external energy supply;

-vehicle-wide activation/deactivation of different driver's consoles of the vehicle;

manual deactivation (emergency release) of the parking brake upon loss of normal operating energy.

These specifications are to be met by the brake cylinder in that the existing service brake is engaged and mechanically locked. The locking mechanism is switched by a so-called control pressure.

Manual deactivation of the parking brake (which is also referred to as parking brake) means: the locking mechanism under the locking force must be released. Since the operating force for manually deactivating the parking brake is usually greater than the manual force of a person, a force transmission ratio is required for the emergency release.

It is also possible that: the control piston must release the locking mechanism under the locking force (e.g., in a towing situation). For this purpose, the piston face of the control piston must be designed such that it generates a sufficient release force at a specific pressure.

Document EP 2826684B 1 describes a brake cylinder for a rail vehicle, in which the parking brake is realized by locking the service brake. In this case, the locking device is arranged inside the service brake pressure chamber. In such brake cylinders with mechanical brake force locking, a manual emergency release device is required, which interrupts the force closure in the locking mechanism in the pressureless state and thus releases the parking brake. An embodiment is described in which the emergency release device acts directly on the control piston. The control piston in turn acts directly on the locking device. The brake cylinder described in EP 2826684B 1 has a relatively small operating piston, the piston force being increased by a downstream mechanical transmission ratio. Whereby the forces acting on the locking device are small.

Disclosure of Invention

It is therefore an object of the present invention to provide a locking device for a mechanical brake force lock for brake cylinders without a rear mechanical transmission ratio, which locking device requires a low actuating force or an emergency release force.

This object is achieved by a brake cylinder according to the invention, in particular for rail vehicles. The brake cylinder according to the invention comprises: a locking device for mechanical brake force locking; and a service brake piston which is axially movable in the housing and which can be moved by means of a pressurized medium and which engages with the piston tube, wherein the piston tube is designed with a non-self-locking thread which engages with a nut which is rotatably mounted in the housing, wherein a locking device interacts with a toothing of the nut, wherein the locking device has one or more pawls, a control piston, an emergency release mechanism and a locking element of the emergency release mechanism. The locking device has an operating device which comprises the control piston, the emergency release mechanism in the form of an emergency release wedge, at least one locking element, at least one energy-accumulating element and a connecting mechanism for manual release.

One inventive concept is: the control mechanism and the emergency release mechanism, which is instead provided with a gear ratio, are arranged such that the control mechanism acts on the emergency release mechanism upon operation thereof. This ensures that the control unit deactivates the locking mechanism with the force transmission ratio.

This results in the following advantages:

-reducing the necessary control force;

-reducing the necessary diameter of the control mechanism;

reducing the necessary installation space.

The brake cylinder of the invention, in particular for rail vehicles, comprises: a locking device for mechanical brake force locking; and a service brake piston which is axially movable in the housing and which can be moved by applying a pressure medium and which engages with the piston tube, wherein the piston tube is designed with a non-self-locking thread which engages with a nut which is rotatably mounted in the housing, wherein a locking device interacts with a toothing of the nut, wherein the locking device has one or more pawls, a control piston, an emergency release mechanism and a locking element of the emergency release mechanism, and wherein the brake cylinder is designed: the locking device has an operating device which comprises the control piston, the emergency release mechanism in the form of an emergency release wedge, at least one locking element, at least one energy-accumulating element and a connecting mechanism for manual release.

The service brake piston can be engaged with the piston tube by the piston being firmly connected to the piston tube (by a screw connection), for example. The service brake piston can also be inserted only loosely. The piston then presses against the end of the piston tube when pressure is applied.

The brake cylinder according to the invention advantageously meets the specifications mentioned at the outset in that the existing service brake is engaged and mechanically locked. The locking device is switched by the control pressure via the operating device or is moved back from the locked state into the released state. The operating device is moved manually in the absence of control pressure and then automatically locked in order to achieve and maintain an emergency release state of the locking device. The manual deactivation of the parking brake (emergency release state) is continuously maintained in order to ensure that the emergency release process is completely ended and the locking mechanism cannot be re-engaged. The emergency release state is cancelled by the control pressure being applied again.

The following particular advantages arise: the emergency release device may be locked continuously, thereby ensuring that the emergency release process can be completely ended.

In a preferred embodiment, the control piston, the emergency release wedge and the at least one energy storage element are arranged one after the other and concentrically to one another with respect to a common control axis. This results in a compact and space-saving construction.

A further embodiment provides that: the control piston, the emergency release wedge and the at least one energy storage element are arranged in the housing in a guide channel so as to be axially slidable in the direction of the control axis. A simple design can thereby be achieved.

In a further embodiment, the control piston is coupled with an emergency release wedge. This is advantageous because the control piston can then act on the locking device via the emergency release wedge by means of its force transmission ratio.

One further embodiment provides for: the control piston is arranged slidably guided relative to the emergency-release wedge at least partially in a first end section of the emergency-release wedge along a longitudinal direction of the emergency-release wedge and a direction of the control axis along a first control direction and along a second control direction opposite to the first control direction. This results in the advantage of a reduced installation space.

If the control piston is guided in a slidable manner in the lower end portion of the emergency release wedge and is preloaded by a spring acting axially in the second control direction, wherein the control piston is held axially in the emergency release wedge by means of an axial stop and is coupled to the emergency release wedge in this way, the control piston can advantageously not only transmit pressure to the emergency release wedge but also assume a further function for controlling the locking element by a relative movement with respect to the emergency release wedge.

Yet another embodiment provides that: the locking element is arranged in a sliding-guided manner and is prestressed by a spring in the direction of its longitudinal axis. This results in a simple structure.

In this way, in one embodiment the longitudinal axis of the locking element can extend perpendicular to the control axis of the control piston, in order to ensure a favorable locking with a stationary component.

The locking element can be arranged in a guide receptacle in the first end section of the emergency release wedge, whereby the space requirement can advantageously be further reduced.

As an alternative, the locking element can also be arranged in the housing. Also considered are: two or more latching elements may be provided, either two or all of which are arranged in the emergency release wedge, or two or all of which are arranged in the housing, or distributed over the emergency release wedge and the housing.

In a further embodiment, the control piston engages with a conical surface with a conical section of the locking element. This is advantageous because the control piston performs its relative movement with respect to the emergency release wedge along a common longitudinal axis, while the locking element, which is pushed by the control piston, moves perpendicularly to said longitudinal axis, so that a simple movement transmission can be achieved.

One embodiment provides for: when the operating device is moved from the inoperative basic position into the release position under the application of a control pressure, the locking device is moved by means of the operating device from a locked state, in which the one or more pawls prevent the nut from rotating about the piston axis by engaging with the teeth of the nut, into a released state, in which the pawls are disengaged from the teeth of the nut and do not prevent the nut from rotating. This makes a compact structure possible.

In a further embodiment, the following possibilities are advantageously provided: when the operating device is moved manually from the inoperative basic position into the emergency release position, the locking device can be moved from the locked state into the release state as an emergency release state, wherein the locking is formed by the locking element. This results in a simple, functional structure.

In a further embodiment, the locking element automatically locks the emergency release wedge of the operating device against the stationary housing in the emergency release position of the operating device. Particularly advantageous here are: the locking element is automatically locked by the pretensioning force of a spring coupled to the locking element when the emergency release position of the operating device is reached.

In a further embodiment, it is particularly advantageous: when the operating device is acted upon by the control pressure in the emergency release position, the operating device is unlocked in the emergency release position of the operating device by means of the locking element. This makes simple control possible without additional control elements.

Yet another embodiment provides that: the control piston, the locking element with the spring and the energy storage element cooperate with one another in such a way that the pressure required by the control piston for unlocking the locking element is less than the force required for sliding the operating device into the disengaged position. This can be achieved, for example, by configuring the spring force of the energy storage element and the spring force of the spring accordingly, wherein the spring force of the spring is smaller than the spring force of the energy storage element. Further factors relevant to this are the taper angle of the conical surface of the control piston and the taper angle of the conical section of the locking element.

Drawings

Embodiments of the present invention will be described below with reference to the accompanying drawings. In the drawings:

FIG. 1 is a schematic longitudinal cross-sectional view of an embodiment of a brake cylinder according to the present invention having a locking apparatus;

FIG. 2 is a schematic cross-sectional view of the locking device in the braking position of the brake cylinder according to the invention along section line II-II of the embodiment shown in FIG. 1;

FIG. 3 is a vertical schematic cross-sectional view of the locking device shown in FIG. 2;

FIG. 4 is a cross-sectional view of the locking apparatus shown in FIG. 3 in an emergency release condition of the brake cylinder according to the present invention;

FIG. 5 is a cross-sectional view of the locking apparatus shown in FIG. 3 in a released or readied position of a brake cylinder according to the present invention; and

fig. 6 is an enlarged view of an operating means of the locking device shown in fig. 2 to 5.

Detailed Description

The concepts "lower", "upper", "left" and "right" are with respect to the arrangement in the respective figures.

Fig. 1 shows a schematic longitudinal section through an exemplary embodiment of a brake cylinder 1 according to the invention, which has a locking device 10.

The brake cylinder 1 has a locking device 10 as a mechanical brake force locking device and is provided for use in a rail vehicle.

The well-known structure and function of brake cylinder 1 will not be explained in further detail here.

A housing interior GR, in which a service brake piston 2 is arranged so as to be slidable along a piston axis 3 in a direction of movement 4, is provided in the housing 1a of the brake cylinder 1.

The service brake piston 2 separates a pressure chamber DR from a housing interior GR of the housing 1 a. The pressure chamber DR is connected to a pressure connection DA, via which pressure medium (e.g., compressed air) can be applied to the pressure chamber DR and thus the service brake piston 2 can be applied.

The service brake piston 2 engages with one end of a piston tube 5, which extends along the piston axis 3 through the housing 1a and is connected to a piston rod, not shown. The engagement of the service brake piston 2 with the piston tube 5 can be achieved in that the service brake piston 2 is firmly connected (by a threaded connection), for example, to the piston tube 5. The service brake piston 2 can also be inserted only loosely. The service brake piston 2 then presses against the end of the piston tube 5 when pressure is applied. The piston rod transmits the braking force to a brake lever (not shown here) of the rail vehicle during braking.

The other end of the piston tube 5 has a threaded section 6 with an external thread, which is firmly connected to the piston tube 5. The thread 9 of the thread section 6, which is arranged on the piston tube 5, engages with the internal thread of a nut 7 mounted in the housing 1 a. The thread 9 is designed to be non-self-locking. The nut 7 is mounted rotatably about the piston axis 3 in an auxiliary section of the housing 1a and is fixed axially.

If the pressure space DR of the brake cylinder 1 and thus the service brake piston 2 are pressurized via the pressure connection DA, the service brake piston 2 is moved together with the piston tube 5 to the left in the direction of movement 4 (in this case in fig. 1).

This axial movement of the service brake piston 2 and the piston tube 5 in the direction of the piston axis 3 causes the nut 7 to rotate about the piston axis 3 due to the non-self-locking threaded engagement of the threaded section 6 with the nut 7. If the nut 7 is prevented from rotating by locking, the service brake piston 2 is prevented from axial movement at the same time. Such locking is formed here by a locking device 10 which cooperates with the external toothing 8 of the nut 7.

The locking device 10 is explained below with reference to fig. 2 to 6.

Fig. 2 shows a schematic sectional view of the locking device 10 in the braking position of the brake cylinder 1 according to the invention along the sectional line II-II of the exemplary embodiment shown in fig. 1. Fig. 3 shows a vertical schematic cross-sectional view of the locking device 10 shown in fig. 2. Fig. 4 shows a sectional view of the locking device 10 shown in fig. 3 in an emergency release state of the brake cylinder 1 according to the invention. Fig. 5 shows a sectional view of the locking device 10 shown in fig. 3 in a position of the brake cylinder 1 according to the invention ready for renewed use. Fig. 6 shows an enlarged view of one operating device 14 of the locking device 10 shown in fig. 2 to 5.

Fig. 2 shows a brake cylinder 1 with a locking device 10. The locking device 10 is designed as a mechanical brake force locking device and has an operating device 14.

The locking device 10 has a locked state (fig. 2 and 3) and a released state (fig. 5).

The operating device 14 has a basic position (fig. 2 and 3), a release position (fig. 5) and an emergency release position (fig. 4).

In the basic position of the operating device 14, the latter is not operated. The locking device 10 is in the locked state.

By applying the control pressure, the actuating device 14 is moved from the basic position into the release position. At the same time, the locking device 10 is in its released state. If the control pressure is removed, the operating device 14 is moved back into its basic position, wherein the locking device 10 is reset back into its locking state.

For the emergency release process in the absence of control pressure, the operating device 14 is manually moved from the basic position into the release position and is automatically locked in this release position, whereby the emergency release position of the operating device 14 is established. While the locking device 10 is released and then in its released state, which is then referred to as the emergency release state and in which the locking device 10 remains.

If the operating device 14 is now loaded with control pressure in its emergency release position, the locking of the emergency release position is released, whereby the release position is reestablished. The locking device 10 continues to remain in its released state in this transition, only with the expression "emergency released" becoming "released". Only when the control pressure of the operating device 14 drops does the operating device 14 reset into the basic position and the locking device 10 reset into the locked state.

When the control pressure has been applied to the actuating device 14 in the release position, the actuating device 14 is moved back into the basic position by a force-storing element 18, which was previously tensioned in the release position.

Fig. 2 and 3 show the locked state of the locking device 10, while fig. 5 shows the released state of the locking device 10.

The operating device 14 can also be referred to as a mechanical release device, by means of which the locking device 10 can be moved from the locked state into the emergency release state (fig. 4) and from the emergency release state into a position ready for renewed use. The position of readying corresponds to the release state (fig. 5).

The emergency release position of the operating device 14 is automatically locked when this emergency release position is reached by means of a locking element 17.

When the operating device 14 is loaded with a control pressure, the control piston 16 unlocks the locking element 17 during the movement of the operating device 14 from the emergency release position into the position ready for resetting.

The locking device 10 then remains in the readied or released state as long as the operating device 14 is loaded with control pressure.

If the application of control pressure to the operating device 14 ends in the release position, the locking device 10 is thereby moved from the release state back into the locking state.

The locking device 10 comprises in this embodiment a threaded section 6 of the piston tube 5, a nut 7, two

pawls

11, 12 and an operating means 14.

The operating device 14 has an emergency release mechanism in the form of an emergency release wedge 15 (which is also referred to as a sliding key), a control piston 16, a locking element 17 and an energy storage element 18. The operating device 14 is also provided with a connecting mechanism 21 for manual operation. This manual operation can be realized, for example, by means of a bowden cable.

The

pawls

11, 12 in this case form locking elements which are arranged opposite the piston axis 3 (with which the nut 7 is arranged coaxially), interact with the toothing 8 of the nut 7 and are actuated by an emergency release wedge 15 of an actuating device 14. The emergency release wedge 15 simultaneously actuates the two

pawls

11, 12.

The locking element 17 locks the emergency release wedge 15 in the emergency release position of the operating device 14 (see fig. 4) on the stationary housing 1 a. When the operating device 14 is pressurized, the locking element 17 is unlocked by the control piston 16 in order to end the emergency release state and to enter the state of readiness for a new or release.

In this way, the control piston 16 deactivates the locking device 10, moving it from the emergency release state (fig. 4) into the readied or released state (fig. 5).

In the locked state of the locking device 10 (fig. 2), the

pawls

11, 12 prevent the nut from rotating about the piston axis 3 by engaging with the teeth 8 of the nut 7, whereas in the disengaged state the

pawls

11, 12 are disengaged from the teeth 8 of the nut 7 and the nut is not prevented from rotating.

The

pawls

11, 12 are configured with two lever arms 11a, 11c, respectively; the toggle levers 12a, 12c are arranged in the housing 1a and are each pivotable about a pivot axis 11e, 12 e. The pivot axes 11e, 12e extend parallel to each other and to the piston axis 3.

The

pawls

11, 12 each comprise a first lever arm 11a, 12a with a

drive end

11b, 12b and a

second lever arm

11c, 12c with a

pawl end

11d, 12 d. The pawl ends 11d, 12d each cooperate oppositely with the teeth of the toothing 8 of the nut 7 in such a way that, in the locked state of the locking device 10, they form a positive lock with the associated teeth, as in a locking mechanism, for example. The nut 7 is a toothed ratchet wheel because its toothed section 8, while the pawl ends 11d, 12d of the

pawls

11, 12 are the corresponding pawl teeth of such a locking mechanism.

In the locked state of the locking device 10, the

pawls

11, 12 are each pressed into engagement with the toothing 8 of the nut 7 by means of a

spring

11f, 12 f. The

springs

11f, 12f are each a compression spring and are held in one spring holder inside the housing 1a and are in contact with the pawl ends 11d, 12d of the

pawls

11, 12, respectively.

The drive ends 11b, 12b of the first lever arms 11a, 12a of the

pawls

11, 12 are equipped with rollers 13. Here, each drive

end

11b, 12b can have a roller 13, or the rollers 13 can be assigned to both drive ends 11b, 12b jointly. The rotational axis of the roller(s) 13 extends parallel to the piston axis 3. Also considered are: the driving ends 11b, 12b slide on the wedges.

The emergency release wedge 15 has a lower end section 15a, also referred to as a first end section 15a, and an upper end section 15b, also referred to as a second end section 15 b. A control piston 16 and a locking element 17 are arranged in the first end section 15 a. Between the first end section 15a and the second end section 15b, an inclined control surface 15c is formed, which points in the longitudinal direction of the emergency release wedge 15 and to the

pawls

11, 12. The control surface 15c tapers from the lower end section 15a of the emergency release wedge 15 to the upper end section 15b of the emergency release wedge 15. The

pawls

11, 12 are in contact with the inclined control surface 15c of the emergency release wedge 15 via the roller(s) 13.

The emergency release wedge 15 forms a power transmission ratio by means of the tilting control surface 15 c.

An intermediate part 20 and a connecting means 21 are attached to the upper end section 15b of the emergency release wedge 15 by means of a fastening section 21a by means of bolts or other fastening elements. The intermediate part 20 is in contact with the lower end of the energy storage element 18, which is designed here as a helical compression spring, and has a collar 20a, which, in cooperation with a circumferential shoulder 19c in the guide channel 19, forms a stop for the actuating device 14. The locked state of the locking device 10 is determined by this stop. In the locked state, the roller/rollers 13 are arranged in the upper end region of the control surface 15c of the emergency release wedge 15. In the released state (not shown) of the locking device 10, the roller/rollers roll downward in a lower end region of the control surface 15c of the emergency release wedge 15, since the emergency release wedge 15 has moved upward when the operating device 14 is moved from the base position into the release position.

In this embodiment, the control piston 16, the emergency release wedge 15 and the energy storage element 18 are arranged in a guide channel 19 in the housing 1a, in a sequential and mutually concentric manner with respect to a common control axis 16a, so as to be axially slidably guided in the direction of the control axis 16 a.

The guide channel 19 has a lower end with a control chamber 19a and extends in the housing 1a through a tubular section which is closed at its upper end by a cover which is not shown. The control chamber 19a is also closed in a pressure-tight manner with respect to the environment by means of a closure cap, not shown. The control chamber 19a communicates with a control pressure connection, not shown.

The control chamber 19a extends between the lower end of the guide channel 19 and an upper position of the control piston 16.

The emergency release wedge 15 and the control piston 16 are arranged in the control chamber 19 a. The control piston 16 is arranged in the lower end section 15a of the emergency release wedge 15 in a slidably guided manner in its longitudinal direction and in the direction of the control axis 16a upward in the first control direction SR1 and downward in the second control direction SR 2. The control piston 16 will be described in more detail below.

A spring chamber 19b is formed between the circumferential collar 19c and the upper end with the cover, in which a force-accumulating element 18 is arranged, which is supported at the lower end on the intermediate piece 20 and at the upper end on the upper cover.

The intermediate part 20 moves with the emergency release wedge 15 and the energy storage element 18 upward in the spring chamber 19b in the first control direction SR1 when entering the release position and downward in the second control direction SR2 when entering the base position. In the locked state, that is to say in the basic position of the actuating device 14, the flange 20a of the intermediate piece 20 rests on the circumferential shoulder 19c of the guide channel 19 and forms a stop in the second control direction SR2, which determines the basic position of the actuating device 14.

In fig. 3, the arrangement of the locking element 17 and the connecting means 21 and the components themselves can be seen in the schematic sectional view of the locking device 10 shown in fig. 2, perpendicular to fig. 2.

The locking element 17 is received in the lower end section 15a of the emergency release wedge 15 in a sliding-guided manner along its longitudinal axis 17f running parallel to the piston axis 3. The details will be described below.

The connecting means 21 is formed in a Z-shape and has a fastening section 21a and an end section 21b extending parallel in opposite directions. The fastening section 21a and the end section 21b are connected via a straight middle section. The connecting means 21 can be formed, for example, as a stamped and bent part from a flat metal material. By means of the connecting mechanism 21, the locking device 10 can be emergency released manually via the operating device 14. In other words, the emergency release wedge 15 can be moved upward in the first control direction SR1 into the emergency release position shown in fig. 4 by means of the connecting means 21.

The end section 21b of the connection 21 is arranged in a shroud 21 c. An upper stop 21d interacts with the end section 21b in such a way that the emergency release position can be determined. Fig. 4 shows this emergency release position of the operating device 14. It can be seen that: the emergency release position of the operating device 14 also corresponds to the release position of the operating device 14. The distinguishing features of these locations are: in the emergency release position, the locking element 17 engages with a retaining receptacle 22 of the housing 1 a.

In the case of such a manual emergency release, the emergency release wedge 15 is moved upward in the control direction SR1 to such an extent that a shoulder 15e of the emergency release wedge 15 comes into contact with the underside of the guide channel 19 surrounding the shoulder 19 c. In this way, the emergency release position of the operating device 14 is determined. In this emergency release position, the locking element 17 comes to rest directly in front of the retaining receptacle 22 of the housing 1a, wherein the longitudinal axis 17f of the locking element 17 is aligned with the center axis of a bore of the retaining receptacle 22.

The energy storage element 18 is compressed in the emergency release position and thus also in the release position. The intermediate piece 20 is moved into the receiving cavity 19b by means of the fastening section 21a of the connecting means 21, the upper end section 15a of the emergency release wedge 15 and a further section.

In this emergency release position, the locking element 17 automatically drops into the hole of the retaining receptacle 22 in the housing 1a, thereby locking the emergency release position of the operating device 14 and thus the release state of the locking device 10. At the same time, the locking element 17 is pressed into the retaining receptacle 22 by means of a spring 17e (as can be seen clearly in fig. 6) in the direction of its longitudinal axis 17 f. The spring 17e constantly loads the locking element 17 with an axial force. The locking element 17 is therefore pressed outward against the inner wall of the guide channel 19 in the basic position (fig. 3) and can automatically engage in the retaining receptacle 22 when the guide element 17 and the retaining receptacle 22 are aligned in the emergency release position (fig. 4).

If the control piston 16 is now acted upon with a control pressure in the emergency release position of the actuating device 14, the control piston 16 is moved in the lower end section 15d (see also fig. 6) of the emergency release wedge 15 in the direction of the first control direction SR1 relative to the stationary emergency release wedge 15 and the conical surface 16d of the control piston 16 displaces the locking element 17 against the force of the spring 17e in such a way that the locking element 17 is disengaged from the retaining receptacle 22 of the housing 1a and is completely retracted back into the emergency release wedge 15 again. The emergency release position is thereby moved back into the release position and is located in the position of the locking device 10 which is again ready, i.e. the disengaged position. This embodiment is particularly compact since the locking element 17 is arranged in the emergency release wedge 15. However, it is also conceivable: the locking member 17 is provided in the housing 1 a.

This is shown in fig. 5. The control piston 16 continues to be displaced by means of the control pressure in the control chamber 19a (between the lower cover and the control piston 16 and the pressure section 16b of the control piston 16) upwards in the first control direction SR 1. At the same time, the locking element 17 is pushed back into the end section 15a of the emergency release wedge 15 by the conical surface 16 d. The details of the locking element 17 and the control piston 16 are illustrated in the enlarged view of fig. 6.

The operating device 14 comprises an emergency release wedge 15, a control piston 16, a locking element 17 and an energy storage element 18. The connecting means 21 for manual actuation also belong to the actuating device here.

The control piston 16 as a control means and the emergency release wedge 15, which is provided with a transmission ratio, are arranged and coupled in succession in that order such that, in the event of a control pressure being applied, the control piston 16 acts on the emergency release wedge 15 in the locked state of the locking device 10 and moves the emergency release wedge 15 in the first control direction SR1 against the force of the energy storage element 18 into the released state. In this way the

pawls

11, 12 of the locking device 10 are deactivated with a force transmission ratio.

When the locked state of the locking device 10 is released manually via the connecting means 21 and no control pressure is present, the manual adjusting force is transmitted directly via the connecting means 21 to the emergency release wedge 15 and moves this emergency release wedge into the emergency release state. At the same time, the control piston 16 is moved together, since it is coupled to the emergency release wedge 15. This coupling will also be explained below.

When the emergency release state is moved into the readiness state again by applying a control pressure to the operating device 14, the control piston 16 acts as a control means on the locking element 17 provided with the transmission ratio. Thereby ensuring that: the control piston 16 deactivates the locking element 17 with the force transmission ratio.

The control piston 16 comprises a pressure section 16b which is connected to a central cylindrical body 16 c. Furthermore, the pressure section 16b is provided circumferentially with a seal, not shown, which divides the control chamber 19a into two regions and seals them depending on the position of the control piston 16. In this way, the region of the control chamber 19a between the lower cover and the pressure section 16b of the control piston 16 is acted upon by the control pressure, while the other region is separated from this region by the seal of the pressure section 16b of the control piston 16.

The central cylindrical body 16c extends through one of the bores 24 of the lower end section 15a of the emergency release wedge 15. A conical surface 16d is formed on the upper end of the central cylindrical body 16 c. As will be explained in more detail below, this conical surface 16d engages an inner conical section 17c of the locking element 17.

A cylindrical guide section 16e is provided on the conical surface 16d of the control piston 16. The cylindrical guide section 16e extends through an elongated hole 17d of the guide element 17 into a guide hole 25 of the receiving section 15d of the emergency release wedge 15. A cylindrical guide section 16e is slidably guided in the guide hole 25 in the direction of the control axis 16a (to which the guide hole 25 is coaxial). The guide opening 25 communicates for venting purposes at its upper end with a channel 26 arranged perpendicularly thereto. The channel 26 opens out as far as the outer side of the emergency release wedge 15.

The locking element 17 is arranged in a slidably guided manner in a guide receptacle 23. The guide receptacle 23 extends parallel to the piston axis 3. The guide receptacle 23 is formed here in the form of a stepped bore into the emergency release wedge 15 and extends transversely to the control axis 16a through the receptacle section 15d of the emergency release wedge 15.

The guide receptacle 23 is provided with an opening (the cross section of which is smaller than the cross section of the guide receptacle 23) on the side directed toward the shield 21d and is open on the opposite side.

The locking element 17 is designed here as a cylindrical pin having a retaining section 17a, an end section 17b, a conical section 17c, an elongated hole 17d and a longitudinal axis 17 f. The holding section 17a is intended to engage with a holding receptacle 22 of the housing 1a in the emergency release state (see fig. 4). The end section 17b is in contact with one end of a spring 17e, the other end of which is supported on the bottom of the guide receptacle 23, which has a smaller opening. In this way, the locking element 17 is prestressed against the housing 1a in the direction of its longitudinal axis 17 f.

A conical section 17c is formed in the underside of the locking element 17 and is in contact with the conical surface 16d of the control piston 16. An elongated hole 17d is formed in the upper side surface of the locking member 17 opposite the conical surface 16 d. The longitudinal axis of the elongated hole 17d extends parallel to the longitudinal axis 17f of the locking element 17 and makes possible a limited movement of the locking element 17 in the direction of its longitudinal axis 17 f.

The control piston 16 is guided in a slidable manner in the bore 24 by means of a cylindrical body 16c in the lower end portion 15a of the emergency release wedge 15 and in a slidable manner in the guide bore 25 by means of a cylindrical guide portion 16e in the receiving portion 15d of the emergency release wedge 15 and is prestressed by means of a spring 16f acting axially in the second control direction SR 2. Furthermore, the control piston 16 is held in the emergency release wedge 15 in the axial direction by means of an axial stop in a manner not shown and is coupled to the emergency release wedge 15 in this way. A spring 16f is arranged between the pressure section 16b of the control piston 16 and the lower end section 15a of the emergency release wedge 15.

The axial stop of the control piston 16 relative to the emergency release wedge 15 limits the axial movement of the control piston 16 in the second control direction SR 2. The position of such an axial stop on the control piston 16 is schematically illustrated by a wide groove below the conical surface 16d of the control piston 16, said groove being aligned with a transversely extending through-hole in the first end section 15a of the emergency release wedge 15. The control piston 16 can thereby perform an axial movement along the control axis 16a, which is limited in the first control direction SR1 on the one hand by a stop in the conical section 17c of the locking element 17 on the locking element 17 and in the second control direction SR2 on the other hand by a not shown axial stop in a transversely extending through-hole in the first end section 15a of the emergency release wedge 15 on the emergency release wedge 15.

When the control piston 16 is displaced in the first control direction SR1 against the force of the spring 16f by the charging pressure, its longitudinal movement in the first control direction SR1 is converted by contact between the conical surface 16d and the inner conical section 17c into a longitudinal movement of the blocking element 17 perpendicular to the longitudinal movement against the force of the spring 17e acting axially on the blocking element 17. At the same time, the locking element 17 engages in the guide receptacle 23 as described above in connection with fig. 5.

Alternatively, the following possibilities can be provided: the locking element 17 is arranged in the housing 1a and is biased by a spring in the direction of the guide channel 19. In the emergency release state, the locking element 17 is then automatically pressed into a receptacle in the emergency release wedge 15. The receptacle may be, for example, a guide receptacle 23. The control piston 16 is then configured to: when the control pressure is applied, it is displaced in the first control direction SR1 as described above and at the same time is inserted into the guide receptacle 23 with an actuating section, which is also conical, for example, and moves the locking element 17 back out of the guide receptacle 23 into the housing 1 a. Although this is not shown, it can be easily imagined.

When the operating device 14 in the basic position is loaded with a control pressure, the control piston 16 first moves into the lower end section 15a of the emergency release wedge 15. The conical surface 16d of the control piston 16 moves upward in the conical section 17c of the locking element 17 and is now only in contact with the conical section 17c, since the locking element 17 is held in the guide receptacle 23 by the inner wall of the guide channel 19 (see fig. 3). Due to the insertion position of the control piston 16, its conical surface 16d, which now engages with the conical section 17c, retains the locking element 17 in the guide receptacle 23.

The control pressure now causes the emergency release wedge 15 to slide in the first control direction SR1 via the control piston 16 inserted in the emergency release wedge 15 until entering the release position. At the same time, the energy storage element 18 is tensioned.

In the release position, automatic locking with the locking element 17 is not achieved with continued application of the control pressure holding the emergency release wedge 15 and the control piston 16 in this release position, since this locking element is retained in the guide receptacle 23 by the control piston 16, i.e. by its conical surface 16d engaging with the conical section 17c of the locking element 17.

The control piston 16, the locking element 17 with the spring 17e and the energy storage element 18 are matched in their dimensions in such a way that the pressure required by the control piston 16 for unlocking the locking element 17 is less than the force required for sliding the operating device 14 into the release position. This can be achieved, for example, by setting the spring force of the energy storage element 18 and the spring force of the spring 17e accordingly, wherein the spring force of the spring 17e is smaller than the spring force of the energy storage element 18. Further factors relevant to this are the taper angle of the conical surface 16d of the control piston 16 and the taper angle of the conical section 17c of the locking element 17.

The invention is not limited by the illustrated embodiments but can be modified within the scope of the claims.

For example, the following can be considered: the locking element 17 does not have a circular cross section, but rather has a different cross section.

List of reference numerals

1 brake cylinder

1a casing

2 service brake piston

3 piston axis

4 direction of motion

5 piston tube

6 thread segment

7 nut

8 tooth part

9 screw thread

10 locking device

11. 12 ratchet pawl

11a, 12a Lever arm

11b, 12b drive end

11c, 12c Lever arm

11d, 12d pawl end

11e, 12e pivot axis

11f, 12f spring

13 roller

14 operating device

15 Emergency release wedge

15a, 15b end section

15c control surface

15d receiving section

15e shoulder

16 control piston

16a control axis

16b pressure section

16c main body

16d conical surface

16e guide section

16f spring

17 locking element

17a holding section

17b end section

17c conical section

17d long hole

17e spring

17f longitudinal axis

18 energy storage element

19 guide channel

19a control chamber

19b spring chamber

19c shoulder

20 intermediate member

20a flange

21 connecting mechanism

21a fastening section

21b end section

21c shield

21d stop

22 holding receptacle

23 guide receiving part

24 holes

25 guide hole

26 channel

DA pressure interface

DR pressure chamber

SR1, SR2 control direction

Claims

1. A brake cylinder (1) comprising: a locking device (10) for mechanical brake force locking; and a service brake piston (2) which is axially movable in the housing (1a) and which can be moved by means of a pressurized medium and which engages in the piston tube (5), wherein the piston tube (5) is designed with a non-self-locking thread (9) which engages in a nut (7) which is rotatably mounted in the housing (1a), wherein a locking device (10) interacts with a toothing (8) of the nut (7), wherein the locking device (10) has one or more pawls (11, 12), a control piston (16), an emergency release mechanism and a locking element (17) of the emergency release mechanism,

the method is characterized in that:

the locking device (10) has an operating device (14) which comprises the control piston (16), the emergency release mechanism in the form of an emergency release wedge (15), at least one locking element (17), at least one energy-accumulating element (18) and a connecting means (21) for manual release.

2. Brake cylinder (1) according to claim 1, characterized in that: the control piston (16), the emergency release wedge (15) and the at least one energy storage element (18) are arranged successively in succession and concentrically to one another in succession with respect to a common control axis (16 a).

3. Brake cylinder (1) according to claim 2, characterized in that: the control piston (16), the emergency release wedge (15) and the at least one energy storage element (18) are arranged in the housing (1a) in a guide channel (19) in an axially slidable manner in the direction of the control axis (16 a).

4. Brake cylinder (1) according to claim 1, characterized in that: the control piston (16) is coupled to the emergency release wedge (15).

5. Brake cylinder (1) according to claim 4, characterized in that: the control piston (16) is arranged in a slidably guided manner relative to the emergency release wedge (15) at least partially in a first end section (15a) of the emergency release wedge (15) in a first control direction (SR1) in the longitudinal direction of the emergency release wedge and in the direction of the control axis (16a) and in a second control direction (SR2) opposite to the first control direction (SR 1).

6. Brake cylinder (1) according to claim 4 or 5, characterized in that: the control piston (16) is guided in a slidable manner in a lower end section (15a) of the emergency release wedge (15) and is preloaded by a spring (16f) acting axially in a second control direction (SR2), wherein the control piston (16) is held axially in the emergency release wedge (15) by means of an axial stop and is coupled to the emergency release wedge (15) in this way.

7. Brake cylinder (1) according to claim 1, characterized in that: the locking element (17) is arranged in a sliding-guided manner and is prestressed by a spring (17e) in the direction of its longitudinal axis (17 f).

8. Brake cylinder (1) according to claim 7, characterized in that: the longitudinal axis (17f) of the locking element (17) extends perpendicularly to the control axis (16a) of the control piston (16).

9. Brake cylinder (1) according to claim 7 or 8, characterized in that: the locking element (17) is arranged in a guide receptacle (23) in a first end section (15a) of the emergency release wedge (15).

10. Brake cylinder (1) according to claim 7 or 8, characterized in that: a locking member (17) is provided in the housing (1 a).

11. Brake cylinder (1) according to any one of claims 1 to 5, characterized in that: the control piston (16) engages with a conical surface (16d) with a conical section (17d) of the locking element (17).

12. Brake cylinder (1) according to any one of claims 1 to 5, characterized in that: when the operating device (14) is moved from an inoperative basic position into a release position under the application of a control pressure, the locking device (10) is moved by means of the operating device (14) from a locked state, in which the one or more pawls (11, 12) prevent the nut (7) from rotating about the piston axis (3) by engaging with the toothing (8) of the nut, into a release state, in which the pawls (11, 12) are disengaged from the toothing (8) of the nut (7) and do not prevent the nut (7) from rotating.

13. Brake cylinder (1) according to claim 12, characterized in that: when the operating device (14) is manually moved from an inoperative basic position into an emergency release position, the locking device (10) is moved from the locked state into a release state as an emergency release state, wherein a locking is formed by the locking element (17).

14. Brake cylinder (1) according to claim 13, characterized in that: the locking element (17) automatically locks an emergency release wedge (15) of the operating device (14) in an emergency release position of the operating device (14) relative to the stationary housing (1 a).

15. Brake cylinder (1) according to claim 13, characterized in that: when the operating device (14) is acted upon by a control pressure in the emergency release position, the operating device (14) is unlocked in the emergency release position of the operating device (14) by means of the locking element (17).

16. Brake cylinder (1) according to claim 12, characterized in that: the control piston (16), the locking element (17) with the spring (17e) and the energy storage element (18) are matched to one another in such a way that the pressure required by the control piston for unlocking the locking element (17) is less than the force required for sliding the operating device (14) into the release position.

17. Brake cylinder (1) according to any one of claims 1 to 5, characterized in that: the brake cylinder (1) is used for a rail vehicle.